JP2003102240A - Combine harvester - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a combine harvester which can use the power of an engine 21 to drive a threshing portion 4 as much as the power loss of a hydraulic speed change mechanism 107 and can easily improve the efficiency of a harvest work, the fuel cost of an engine 21, and the like. SOLUTION: This combine harvester, in which the hydraulic speed change mechanism 107 for transmitting the power of the engine 21 is disposed in a transmission case 23, is characterized by disposing a vehicle speed-synchronizing shaft 72 for synchronizing with a vehicle speed through the hydraulic speed change mechanism 107 to drive a reaping portion 8, further disposing a constant rotation shaft 71 for directly transmitting the driving force of the engine 21, and selecting either of the vehicle speed-synchronizing shaft 72 and the constant rotation shaft 71 to drive the reaping portion 8.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a combine for continuously cutting and threshing grain culms.

[0002]

Conventionally, there is a technique for transmitting harvesting work by transmitting engine driving force to a mission case that drives a threshing section, a mowing section and a traveling crawler. The structure in which the engine output shaft is oriented in the left-right direction and the power is transmitted through the bevel gear to the handle cylinder by changing the direction by 90 degrees, a bevel gear that withstands the large horsepower required for the handle cylinder is provided, and the oil temperature of the bevel gear installation part is increased. Has risen and the durability is insufficient. In addition, a counter case that supports a fixed rotating shaft (counter shaft) is provided, the output shaft of the transmission case side and the constant rotating shaft are connected by a belt, and the wet clutch in the counter case is turned on to pour the mowing section. In the structure that obtains the driving force, the constant rotation system and the vehicle speed tuning system are separated from each other, so that belt transmission is indispensable, and there is a problem that the engine tends to be rotated along with the wet clutch by operating the engine. Further, in the structure in which the transmission case hydraulic speed change mechanism is provided, the mowing unit is driven by vehicle speed synchronization via the hydraulic speed change force, so that even if the substantial power required for the mowing unit is about 10% of engine horsepower, About 14 percent is required for the hydraulic transmission mechanism that outputs the driving force of the section, resulting in a power loss of 4 percent. Further, in the structure in which the hydraulic motor of the hydraulic speed change mechanism is made variable so as to be the sub-transmission means, the relative speed between the mowing part and the traveling crawler (vehicle speed) is changed by switching the sub-transmission to cope with harvesting of fall culms. Therefore, there is a problem that switching of the auxiliary shift is troublesome and the speed (vehicle speed) when the auxiliary shift is low becomes slow. In addition, an axis that transmits power to the mowing section, an axis that transmits power to the selection mechanism,
In the structure in which each shaft for transmitting power to the feed chain is separately installed, the cost of assembling each shaft is high, maintenance is disadvantageous, and there is a problem that the structure for synchronizing the vehicle speed of the feed chain cannot be easily configured. Also, the loss of horsepower of the hydraulic transmission installed in the mission case is about 1 of engine power.
In the structure of 0%, the power of the engine is wasted or the fuel efficiency is deteriorated, the capacity of the oil cooler for lowering the oil temperature must be increased, and there is a problem that the worker feels insufficient horsepower.

[0003]

SUMMARY OF THE INVENTION Therefore, the present invention is a vehicle speed tuning shaft for driving a reaper in synchronization with a vehicle speed via a hydraulic speed change mechanism in a combine in which a hydraulic speed change mechanism for transmitting engine power is provided in a transmission case. And a constant rotation axis that directly transmits the driving force of the engine, and selects either the vehicle speed tuning axis or the constant rotation axis to drive the mowing section, and when the mowing work reaches the maximum speed state. When the vehicle speed synchronous rotation is switched to constant rotation, and the reaper is driven to rotate at a constant speed so that the volumetric efficiency of the hydraulic speed change mechanism is 100%, the rotational speed at constant speed is higher than that at the vehicle speed synchronous rotation. The speed change mechanism does not work to drive the mowing section, and the efficient mechanical drive system drives the mowing section, and the engine power is used to drive the threshing section by the loss of the hydraulic speed change mechanism. Obtained, those obtained aim to facilitate and improve harvesting efficiency and fuel economy improvement of the engine.

Further, a constant rotating shaft for branching the driving force of the handle cylinder and a vehicle speed synchronizing shaft are provided in the counter case in close proximity to each other in a substantially parallel manner, and the pouring driving force for pouring the reaper is supplied from the constant rotating shaft. It is configured so that it can be input to the vehicle speed tuning shaft, for example, the conventional belt transmission that transmits the pouring drive force is not required, and the pouring drive structure of the cutting unit can be simplified and the size and cost can be easily reduced. The pouring drive force can be turned on and off by the claw clutch to prevent entrainment and reduce the response delay, and the pouring drive of the mowing part is performed at 50 to 80% of the maximum speed to prevent clogging and reduce work time loss. I will get it.

Further, a mowing gear changing mechanism for changing the driving speed of the mowing section is internally provided in the counter case. By changing the mowing gear changing while keeping the auxiliary gearshift at the standard (low speed), an felling grain culm or the like can be obtained. Correspondingly, the mowing work can be performed,
For example, there is no trouble of controlling the auxiliary shift changing means by the variable hydraulic motor configured by making the hydraulic motor of the hydraulic speed change mechanism variable, and the harvesting speed change mechanism can be changed over even during work so that a part of the rice grain Even when the user is lying down, the vehicle speed synchronization speed of the mowing unit can be changed to an appropriate speed, and by using the neutral of the mowing speed change mechanism as a mowing clutch, it is not necessary to provide a mowing clutch separately, and the mowing input belt is always provided. The tension structure can be used to improve durability.

Further, a rotational force equal to or higher than the rotational speed of the vehicle speed tuning input from the mission case is configured to be able to be input from the constant rotating shaft to the vehicle speed tuning input shaft. When the speed change means is formed,
By switching the rotation of the mowing unit from vehicle speed synchronization to a constant rotation at the highest working speed, the hydraulic pressure of the hydraulic speed change mechanism can be reduced by the difference in the number of rotations to improve the efficiency. When a mechanical sub-transmission means is formed by, the rotation of the mowing part can be freely increased by switching to constant rotation near the maximum work speed, and switching from vehicle speed synchronization to constant rotation and pouring of the mowing part can be performed. By selectively performing the switching to turn the drive on and performing only one of the constant rotation and the pouring drive, it is possible to eliminate the problem that two inputs having different rotational speeds are simultaneously transmitted to the cutting unit, Moreover, in the structure provided with the sub-transmission means using the variable hydraulic motor, even if the rotation speed of the mowing unit is increased by changing the gear shifting of the mowing unit from low to high, this rotation becomes excessively high. The way up, it is possible to switch to a fixed rotation from the vehicle speed tuning is to obtain aim to facilitate and improve and reduce the driving noise of the durability.

Further, in the combine in which the hydraulic transmission mechanism for transmitting the power of the engine is provided in the transmission case, a constant rotating shaft is provided on the lower side of the threshing clutch for transmitting the engine power in the threshing portion, and the power of the constant rotating shaft is supplied by the hydraulic transmission mechanism. Is provided with a constant rotation mechanism and a constant rotation clutch, which transmits the engine output to the output side of the hydraulic speed change mechanism through the constant speed mechanism at the maximum work speed, so that the hydraulic pressure of the hydraulic speed change mechanism is charged. It is possible to eliminate the hydraulic transmission loss, reduce the power loss of traveling drive by the hydraulic transmission, improve the fuel efficiency of the engine, and form the oil cooler of the hydraulic transmission to a small capacity. Even if the traveling load increases, such as when changing the direction of the vehicle, the operator can perform driving operations without feeling insufficient traveling power, and It is possible to easily reduce the speed, etc., recover the power loss of the hydraulic speed change mechanism and drive the traveling crawler with high efficiency at the maximum speed, and enable the maximum speed work with a sufficient driving force to improve the driving operability. It can be easily planned.

Further, when the working vehicle speed transmitted via the hydraulic speed change mechanism is close to the maximum speed, the constant rotation clutch is manually or automatically turned on. By turning on the constant rotation clutch, the volumetric efficiency of the hydraulic speed change mechanism ( Generally, the vehicle speed (about 5%) is increased by the difference between the constant rotation output (generally 75%) and the constant rotation output (generally 90%). The engine power can be used to drive the working unit, and the power required for the highest speed work can be easily secured.

Further, the volumetric efficiency of the hydraulic transmission is about 100.
It transmits a driving force with a rotation speed that is almost the same as the rotation speed that is a percentage from the constant rotation mechanism.By designing the engine power according to the work maximum speed, there is a margin of power up to the maximum speed, but the maximum speed In this condition, when there is almost no leeway in power, the same effect can be expected when the engine horsepower is increased by recovering the power loss, and it is possible to easily secure the power required for maximum speed work. is there.

Further, the constant rotation clutch is automatically disengaged when the work vehicle speed decreases from around the maximum work speed. By designing the engine power in accordance with the maximum work speed, the power can be increased to near the maximum work speed. Since there is a margin, for example, even if the operator does not recognize that the work vehicle speed has decreased from the work maximum speed, the work vehicle speed can be reduced by simply performing an operation to reduce the work vehicle speed at the highest speed with almost no power. It is possible to automatically release the highest speed working state due to the decrease of the engine, and it is possible to easily improve the durability of the engine and the fuel consumption.

[0011]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 is an overall left side view of the combine, and FIG. 2 is a plan view thereof. In the figure, 1 is a track frame on which a traveling crawler 2 is installed, 3 is a machine frame installed on the track frame 1, 4 is a feed chain 5 A threshing unit which is a threshing machine which is stretched on the left side and has a handling cylinder 6 and a processing cylinder 7 built-in, 8
Is a mowing unit including a cutting blade 9 and a grain culm transport mechanism 10 and the like, 1
Reference numeral 1 is a hydraulic cylinder for moving up and down the mowing unit 8 via the mowing frame 12, 13 is an straw processing unit for exposing the end of the straw chain 14, and 15 is carrying in the grains from the threshing unit 4 through the hoisting barrel 16. Grain tank, 17 is a discharge auger for discharging the grain in the tank 15 to the outside of the machine, and 18 is the operation handle 1
An operation cabin provided with 9 and a driver's seat 20 is an engine provided below the operation cabin 18, and is configured to continuously cut and dehull grain culms.

Further, as shown in FIGS. 4 to 6, the engine 21 is provided in an engine room cover 22, and the front, rear, left and right side surfaces and the upper surface of the engine 21 are covered with the engine room cover 22, and the engine 21 is provided.
Outside of the cover 22 in front of the mission case 2
3 and the radiator 24, and the universal joint shaft 25 between the engine 21 and the transmission case 23.
Driving force is transmitted to the mission case 23, the drive sprockets 27 of the left and right traveling crawlers 2 are axially supported on both sides of the mission case 23 via the axle case 26, and the cooling fan 28 of the radiator 24 is mounted on the right side surface of the mission case 23. Provided, radiator 24 and oil cooler 2
9 is cooled by the cooling fan 28.

The output shaft 30 of the engine 21 is provided on the front side and the rear side of the engine room cover 22, the universal joint shaft 25 is connected to the front side of the output shaft 30, and the work is performed on the rear side of the output shaft 30. In addition to providing the output pulley 31, a counter case 32 is provided on the upper surface of the machine stand 3 in front of the threshing unit 4 on the left side of the engine 21, and the input pulley 33, the vehicle speed tuning pulley 34, the threshing pulley 35, the reaping pulley 36, and the sorting pulley 3 are provided.
7 is pivotally supported on the counter case 32, the input pulley 33 on the rear side of the case 32 is connected to the work output pulley 31 by the belt 38, and the driving force of the engine 21 is transmitted to the counter case 32. In addition, the mowing drive pulley 3 of the mission case 23
9 is a vehicle speed tuning pulley 34 on the right side of the counter case 32.
The belt 40 is connected, and the support base 41 is erected on the front upper surface of the machine base 3, and the reaping 1-axis case 42 is attached to the support base 41.
Is rotatably supported, the mowing frame 12 is connected to the case 42, and the mowing section 8 is rotated around the case 42 to move up and down.
3, the reaping input pulley 44 is pivotally supported, and the reaping pulley 36 on the left side of the counter case 32 is reaped by the reaping input pulley 4
4 is connected to the belt 45, and the driving force is transmitted to each part of the mowing unit 8.

Further, the threshing pulley 35 on the front side of the counter case 32 is connected to the belt 48 by the drive input pulleys 46 and 47 of the handling cylinder 4 and the processing cylinder 7, and the sorting tray 49 and the swing sorting mechanism on the lower side of the handling barrel 4 are connected. The driving force is transmitted from the sorting pulley 37 to drive each part of the threshing unit 4, and the feed chain input shaft 50 is provided on the left side surface of the counter case 32.
Power is transmitted from the input shaft 50 to the drive sprocket 51 of the feed chain 5 that can move outward. Further, a discharge driving pulley 52 is provided on the front side of the grain tank 15, the pulley 52 is belt-connected to the work output pulley 31 via a discharge clutch, and the output of the engine 21 is transmitted to the discharge auger 17 to transmit the grain of the tank 15 to the grain. Is discharged.

Further, a ventilation duct 53 is connected to the front side of an engine room cover 22 having a hermetically sealed structure in which the engine 21 is installed, and a wind tunnel type dust removing case is provided on the outer side surface on the right side of the engine room cover 22 and the front radiator 24. 54, the dust removal case 54 is rotatably mounted around the rear fulcrum shaft, the outside air intake is opened above the rear part of the right side of the dust removal case 54 (outside of the machine), and the left side of the dust removal case 54 (inside of the machine) The radiator side filter and the ventilation side filter are joined below the front part. Then, the cooling fan 28
The outside air is taken from the dust removing case 54 through the filter into the oil cooler 29 and the radiator 24 to be cooled, and the output shaft 30 is belt-connected to the generator pulley and the fan pulley in the front part of the engine 21, and the front side of the fan pulley is connected. A ventilation fan 55 is provided (on the same axis), a ventilation fan 55 is provided at a connection portion between the engine room inside the engine room cover 22 and the ventilation duct 53, and the outside air taken into the dust removal case 54 from the outside air intake port is a ventilation fan. The air is supplied to the inside of the hermetically closed engine room cover 22 through the ventilation duct 53 by 55 to ventilate the engine room.

Further, as shown in FIG. 6, the first conveyor 56 for taking out the grains to the tank 15 is provided at the rear side of the sorting Kara 49, and the second conveyor 57 for taking out the second sorted matter to be re-sorted and the sub conveyor. A swinging sorting board 5 in which a Kara 58 is further provided on the rear side and is placed horizontally between the handling cylinder 6 and the conveyors 56, 57.
9, a sorting mechanism 60 is configured below the handling cylinder 6, and power is transmitted from the sorting pulley 37 to the sorting mechanism 60 via the sorting input belt 61.

Further, as shown in FIG. 7 to FIG. 13, the handling case input shaft 62 is pivotally supported by the counter case 32, and the shaft 62 is extended in the front-rear direction, and the front side of the shaft 62 outside the front surface of the counter case 32. The threshing pulley 35 is provided in the rear of the counter case 32, and the input pulley 3 is provided on the rear side of the shaft 62 on the outer side of the rear surface.
3, the belt 38 is tensioned between the pulleys 31 and 33 via the tension roller type threshing clutch 63 to input a constant rotational power. In addition, a pair of left and right anti-vibration rubber 6
The engine 21 is mounted via the 4/65, the belt 38 is driven and output from the rear side of the output shaft 30 on the flywheel 66 mounting side, and the drive shaft is driven from the front side of the output side 30 on the mounting side of the gear case 67 via the universal joint shaft 25. Output, and the rear anti-vibration rubber 65 is higher than the spring constant of the front anti-vibration rubber 64.
The spring constant of 6 is formed to be large, and the rear anti-vibration rubber 65 receives the reaction force against the lateral load of the drive of the belt 38 on the flywheel 66 side, and the front anti-vibration rubber 6 does not receive the lateral load.
The vibration-proofing effect of No. 4 is increased to ensure constant vibration, low noise, durability against the reaction force of the belt 38, and the like.

Further, as shown in FIG. 7, a tuning input shaft 68 is pivotally supported on the right side of the counter case 32, and a vehicle speed tuning pulley 34 is provided on the right side of the shaft 68 outside the counter case 32. The belt 40 is tensioned between the pulleys 34 and 39 via the clutch 69 to input the vehicle speed tuning power from the transmission case 23 to the counter case 32.

Further, as shown in FIG. 10 and FIG. 13, a constant rotation shaft 71, which is a counter shaft or a selection input shaft for connecting the right side of the handling cylinder input shaft 62 to the bevel gear 70, and substantially parallel to the front side of the shaft 71. The provided vehicle speed tuning shaft 72 and the counter case 32 are pivotally supported, and the harvesting transmission mechanism 73 is provided.
The low speed gear 74 and the high speed gear 75 forming the
The gears 74 are provided between the first gear 72 and the second gear 72 by the cutting gear shifting slider 76 for performing the low gear cutting, the neutral gear cutting, and the high gear cutting gear shifting.
-75 is selectively engaged with the vehicle speed tuning shaft 72 to perform the mowing shift. Further, the tuning input shaft 68 is attached to each of the gears 74 and 75.
A one-way clutch 77 for transmitting the vehicle speed tuning rotational force and a ball clutch type direct drive clutch 78 for engaging and disengaging the gears 74 and 75 with the tuning input shaft 68 are provided on the tuning input shaft 68. The power from the tuning pulley 39 is transmitted to the vehicle speed tuning shaft 72 by the one-way clutch 77, while the tuning input shaft 68 and the vehicle speed tuning shaft 72 are directly rotated by the driving clutch 78 via the gears 74 and 75. Constitute.

Further, the pouring gear 80 and the high speed cut gear 81 forming the constant rotation mechanism 79 are connected to the shafts 7 1 and 7 respectively.
2 and a switching slider 82 for pouring drive or high-speed cutting drive of the reaper 8 by means of a switching slider 82.
The gears 80 and 81 are selectively engaged with the gear 72, and the cutting unit 8 is driven to flow to convey the grain culms of the cutting unit 8 to the feed chain 5 side irrespective of the traveling state, while the cutting unit 8
Is driven at a high speed to drive the reaping unit 8 at a constant rotation speed higher than the maximum speed of vehicle speed synchronization to cut the lodging grain culm.

Further, the left end of the constant rotation shaft 71 is made to project to the rear side of the lower part on the left side of the counter case 32, and
The sorting pulley 37 is pivotally supported on the left end portion. Further, the reaping input shaft 83 is pivotally supported on the lower front side on the left side of the counter case 32, the right side of the shaft 83 is connected to the vehicle speed tuning shaft 72 by a gear 84, and the shaft 83 is projected to the left side of the counter case 32.
The reaping pulley 36 is rotatably supported on the left end of the reaper, the reaping drive shaft 85 is connected to the reaper 1 shaft 43 by the gear 86, and the reaper input shaft 44 is rotatably supported by the reaper drive shaft 85. Through the fulcrum shaft 87 to the gear case 8
8 is rotatably provided around the vertical axis, the left side of the reaping 1-axis case 42 is detachably fixed to the gear case 88, and the gear 86 is internally provided in each of the cases 42 and 88. From the left end side of the reaping 1-axis 43. The reaping power is input to drive the reaper 8 via the reaper 2 shaft 89 which is inserted into the reaper frame 12 on the right end side of the case 42, while the reaper 8 is horizontally arranged around the fulcrum shaft 87 on the left side of the machine body. It is rotated and moved to perform maintenance and the like near the cases 23 and 32 inside the machine body.

Further, the feed chain input shaft 50 is pivotally supported on the upper left side of the counter case 32, and a feed chain clutch 90 is provided.
1, the input shaft 50 is connected to the chain 92, and a feed chain transmission mechanism 93 for transmitting the rotation of the constant rotation shaft 71 by changing the rotation speed of the vehicle speed tuning shaft 72 is provided, and the sun gear 94, the planetary gear 95, and the ring gear 9 are provided.
The planetary gear mechanism 97 including 6 forms the mechanism 93 in a continuously variable manner. The sun gear 94 is engaged with the fixed rotating shaft 71, and the ring gear 96 that is supported by the fixed rotating shaft 71 in an idling manner is synchronized with the vehicle speed. A shaft bearing 72 is coupled to the shaft 72, and a bearing 99 for freely supporting the planetary gear 95 is supported for free rotation on the constant rotating shaft 71, and the feed chain drive shaft 9 is fed through the feed chain clutch 90.
1, the bearing body 99 is connected to the gear 100 to ensure the minimum rotation required for the transportation of the grain, and the feed chain 5 speed can be changed from low constant rotation to high rotation in synchronization with the vehicle speed. .

Further, as shown in FIG. 9, the mowing variable speed slider 7
6, and a hydraulic direct drive cylinder 102 that engages the direct drive clutch 78.
The fixed hydraulic rotation cylinder 103 that operates the switching slider 82 and the hydraulic feed chain cylinder 104 that disconnects the feed chain clutch 90 are fixed to the upper surface and the front surface of the counter case 32.

Further, as shown in FIGS. 7 and 17, a continuously variable hydraulic speed change mechanism 107 including a hydraulic pump 105 and a motor 106, and a hydraulic steering mechanism 110 including a hydraulic pump 108 and a motor 109 are provided in the mission case 23, so that the transmission case 23 can be freely operated. The engine 21 power transmitted via the joint shaft 25 drives the pumps 105 and 108 to change the speed of the pump 10 for shifting.
5, the main speed change lever 112 is connected to the variable output swash plate 111, and the mechanical gear auxiliary speed change mechanism 113 is provided on the output side of the speed change motor 106.
And the steering handle 19 is connected to the output variable swash plate 115 of the pump 108 for steering.
The output of 06.109 is forcibly differentially output from the planetary gear mechanism 116, the left and right traveling crawlers 2 are driven, and each traveling operation of forward and backward and left and right turns is performed, and the motor 106 for continuously variable transmission The mowing drive pulley 39 is pivotally supported on the output shaft 117, and the main shift output of the continuously variable transmission mechanism 107 is transmitted from the pulley 39 to the counter case 32. Further, as shown in FIG. 18, an auxiliary transmission lever 114 is connected to the variable output swash plate 117 of the transmission motor 106, and the auxiliary transmission lever (114) switches the auxiliary transmission sensor (127) to switch the auxiliary transmission motor (illustration). 17) may be operated to switch the swash plate (117) to high speed or low speed by the motor to omit the gear auxiliary transmission mechanism 113 of FIG. 17. In this structure, the auxiliary transmission output of the motor 106 may be omitted. Is transmitted from the pulley 39 to the counter case 32.

Further, as shown in FIG. 19, a threshing sensor 119 for detecting the threshing clutch 63 on the threshing clutch lever 118, a mowing sensor 121 for detecting the mowing clutch 69 on the mowing clutch lever 120, and a mowing gear shifting lever 122. The mowing gear change sensor 123 for detecting switching of the mowing gear change slider 76 between low speed, neutral and high speed, and the main gear change lever 1.
12, a main shift sensor 124 for detecting forward / neutral / reverse switching, a manual pouring sensor 126 for detecting a stepping operation of a pouring pedal 125 by an operator, and a low / neutral / high speed switching of the auxiliary shift lever 114. The changeover switch type auxiliary shift sensor 127 is connected to the work controller 128 composed of a microcomputer.

Further, the direct drive switch 129 for manually switching the operation to drive the reaper 8 by the constant rotation output of the engine 21, and the speed (vehicle speed) of the left and right traveling crawlers 2.
Left and right vehicle speed sensors 130 and 131 for detecting the presence and absence, and a grain culm sensor 132 for detecting the presence or absence of the transport grain culm of the reaping unit 8,
Mowing input sensor 133 for detecting the driving speed of the mowing unit 8
And low-speed and high-speed reaping solenoids 134 and 135 for switching the reaping transmission cylinder 101 to low speed or high speed,
A feed chain solenoid 136 that operates the feed chain clutch cylinder 104 to disengage the feed chain clutch 90, a flow solenoid 137 that causes the switching slider 82 to engage the flow gear 80 by the constant rotation cylinder 103, and a constant rotation cylinder 103.
The high-speed cut solenoid 138 for engaging the high-speed cut gear 81 with the switching slider 82 and the direct drive solenoid 139 for directly operating the direct drive cylinder 102 into the direct drive clutch 78 are connected to the work controller 128, and the flow chart of FIG. So that the reaper 8
Is operated at a pouring speed, a high speed cutting speed, or a vehicle speed synchronizing speed, and a constant rotational force is transmitted from the counter case 32 to the output side of the hydraulic motor 106 of the hydraulic speed change mechanism 107 so that the rotation speed is higher than the output of the motor 106. The traveling crawler 2 is directly driven without using the mechanism 107.

As is apparent from the above, in the combine provided with the counter case 32 for transmitting the driving force of the engine 21 to the handling case 6, the handling case input shaft 62 provided in the counter case 32 is extended in the machine longitudinal direction. Then, the handling cylinder input shaft 62 is passed through in the front-back direction of the counter case 32,
The engine 21 is connected to the belt 38 at one end of the handling cylinder input shaft 62, and the handling barrel 6 is connected to the belt 48 at the other end of the handling cylinder input shaft 62.
It is not necessary to provide a bevel gear, which is inefficient, in the drive system of the handling cylinder 6 that is coupled and uses only the counter case 32 as the bearing of the handling cylinder input shaft 62, and requires a large horsepower. By preventing the internal oil temperature of the counter case 32 from rising and changing the length of the handle barrel input shaft 62, the position of the handle barrel 6 in the front-rear direction or the length of the handle barrel 6 in the front-rear direction is changed. The counter case 32 is commonly used for various models to reduce the manufacturing cost.

Further, a constant rotating shaft 71, which is a counter shaft connected to the handle barrel input shaft 62, is provided in the counter case 32 to take out power to the side of the machine body, and the constant rotating shaft 71 is extended to the left side of the machine body. The power of the sorting mechanism 60 of the threshing unit 4, the feed chain 5, and the cutting unit 8 is set to a constant rotation shaft 71.
Output from the left side of the threshing clutch 63, and the threshing clutch 63 is turned on and off to drive or stop the sorting mechanism 60 at the same time as the handling cylinder 6, and the small rotating bevel gear 70 capable of increasing efficiency and durability improves the constant rotation shaft 71 of low power. Input shaft 62
And the power source of the feed chain 5 or the mowing unit 8 is attached to the left side of the machine body, and the vehicle speed tuning shaft 72 for driving the mowing unit 8 at the vehicle speed synchronizing speed is attached to the counter case 32.
The vehicle speed tuning shaft 72 is provided substantially in parallel with the constant rotation shaft 71, and the feed chain 5 is driven by the constant rotation output from the constant rotation shaft 71 and the variable output from the vehicle speed tuning shaft 72 to keep the constant rotation. The feed chain 5 drive system that drives the feed chain 5 while keeping it in sync with the vehicle speed is simplified, downsized, and costs are reduced. The drive system and the drive system of the selection mechanism 60 are arranged in an efficient layout.

Further, a feed chain input shaft 50 for transmitting a driving force to the feed chain 5 and a feed chain transmission mechanism 93 for changing the driving speed of the feed chain 5 in synchronization with the vehicle speed are provided in the counter case 32 so that the low speed side is kept constant. The rotation of the feed chain 5 that maintains the lowest rotation speed is increased by the vehicle speed tuning input, and the power is transmitted to the feed chain 5 on the lower side of the drive system of the cutting unit 8, thereby cutting the cutting unit. The rotation of the feed chain 5 and the rotation of the feed chain 5 are maintained relatively constant to ensure good transfer and inheritance performance of the cut grain culm, and the feed chain 5
The belt 45 of the mowing section drive system, which is on the lower side of the position where the power is branched, is always tensioned to have a constant drive structure without a power cutting member such as a clutch, and the mowing section 8 cannot physically rotate in the reverse direction. With the structure, the drive load of the mowing unit 8 serves as a brake under the condition that the drive input to the mowing unit 8 is neutral, and the state in which the feed chain speed change mechanism 93 outputs the constant rotation at the lowest speed is maintained. , Connect the drive of constant rotation of the feed chain 5.

Further, the sorting input shaft 71 for transmitting the driving force to the sorting mechanism 60 of the threshing unit 4, and the cutting unit 8 in synchronization with the vehicle speed.
In the combine in which the vehicle speed tuning shaft 72 that drives the drive chain and the feed chain input shaft 50 that transmits the driving force to the feed chain 5 are provided, the rotation of the selection input shaft 71 is controlled by the vehicle speed tuning shaft 72.
Is provided with a feed chain speed change mechanism 93 that changes gears according to the change in the number of revolutions, to secure the speed of the feed chain 5 even at low speed work, and to reduce the power required for threshing by thinning the threshing straw layer during high speed work. Planetary gear mechanism 9 including a planetary gear 95 and a ring gear 96
7, a feed chain transmission mechanism 93 is formed, a sun gear 94 is driven via a selection input shaft 71, a ring gear 96 is rotated via a vehicle speed tuning shaft 72, and a feed chain input shaft 50 is fed to a feed chain input shaft 50 via a planetary gear 95. 5 driving force is transmitted, the sun gear 94 is arranged on the lower side of the threshing clutch 63, the feed chain 5 is driven only when the handling cylinder 6 is driven, and the speed of the feed chain 5 is synchronized with the vehicle speed from low constant rotation to high rotation. In order to prevent jamming of transport straw during low-speed work and threshing overload during high-speed work, etc.

Further, a reaping input shaft 83 connected to the constant rotation shaft 71 which is a selection input shaft and the vehicle speed tuning shaft 72 is provided on the lower front side of the counter case 32, and the constant rotation shaft 71 is provided on the lower rear side of the counter case 32. The feed chain input shaft 50 is provided on the upper portion of the counter case 32, and the drive of the mowing unit 8 and the threshing unit 4 is integrated in the counter case 32 to simplify the maintenance work and reduce the manufacturing cost. Each of the transmission systems of the mowing section 8, the sorting mechanism 60, or the feed chain 5 is divided into upper parts, and the feed chain 5 is driven at a speed synchronized with the vehicle speed while ensuring a constant minimum speed, and at the same time, the mowing section. When the driving speed of the mowing section 8 becomes slower under the condition that there is a transported grain culm in the cutting section 8, the operation of driving the mowing section 8 at the pouring speed is automatically performed. Compared by pedal 125 pouring such as the one which manually operated pouring reaper 8 only operation, eliminating the problem of timing or forgets the operation pouring deviates prevents culms that clogged.

Further, in the combine in which the hydraulic speed change mechanism 107 for transmitting the power of the engine 21 is provided in the transmission case 23, the vehicle speed tuning shaft 72 for driving the reaper 8 in synchronization with the vehicle speed via the hydraulic speed change mechanism 107, and the engine 21. The constant rotation shaft 71 for directly transmitting the driving force is provided, and either the vehicle speed tuning shaft 72 or the constant rotation shaft 71 is selected to drive the cutting unit 8. Then, when the mowing work reaches the maximum speed, the vehicle speed synchronized rotation is switched to a constant rotation,
When the mowing unit 8 is driven to rotate at a constant speed at a rotation speed at which the volumetric efficiency of the hydraulic speed change mechanism 107 becomes 100%, the number of rotations at the constant speed becomes higher than the rotation of the vehicle speed tuning, and the hydraulic speed change mechanism 107 causes the hydraulic speed change mechanism 107 to drive the mow unit 8. Do not work to drive,
The cutting machine 8 is driven by an efficient mechanical drive system,
The power of the engine 21 can be utilized to drive the threshing unit 4 by the loss of the hydraulic speed change mechanism 107, and the efficiency of the harvesting work and the fuel consumption of the engine 21 can be improved.

Further, a constant rotation shaft 71 for branching the driving force of the handle cylinder 6 and a vehicle speed tuning shaft 72 are installed in the counter case 32 in close proximity to each other in a substantially parallel manner, and the pouring driving force for pouring the cutting unit 8 is operated. Is configured to be able to be input to the vehicle speed tuning shaft 72 from the constant rotation shaft 71, and, for example, the conventional belt transmission for transmitting the pouring drive force is not required, and the pouring drive structure of the reaper 8 is simplified and is compact and the cost is low. Then, the pouring driving force is turned on and off by the claw clutch 79 to prevent accompanying rotation and reduce the response delay, and the cutting unit 8 is pouring driven at 50 to 80% of the maximum number of rotations to prevent clogging and reduce the working time. A mowing gear change mechanism 73 for reducing the loss and changing the driving speed of the mowing unit 8 is internally provided in the counter case 32, and the mowing gear change is performed in a state where the auxiliary gear shift is maintained at a standard (low speed). Complete reaper corresponding like lodging culms by switching, for example, a hydraulic transmission mechanism 107
There is no trouble of controlling the sub-transmission changing means by the variable hydraulic motor 106 that is configured by making the hydraulic motor of the variable type. Even if the work is performed in the state, the vehicle speed synchronizing speed of the mowing unit is changed to an appropriate speed, and the neutral of the mowing speed change mechanism 73 is also used as a mowing clutch, so that it is not necessary to separately provide a mowing clutch, and the mowing input belt 45 is always tensioned. The structure will improve durability.

A rotational force equal to or higher than the rotational speed of the vehicle speed tuning input from the mission case 23 can be input to the vehicle speed tuning input shaft 72 from the constant rotation shaft 71. For example, the hydraulic motor 106 of the hydraulic speed change mechanism 107 is variable. When the sub-transmission means is formed by changing the rotation of the mowing unit 8 from the vehicle speed synchronization to the constant rotation when the working speed is the highest, the hydraulic pressure of the hydraulic speed change mechanism 107 is reduced by the difference in the number of rotations to improve the efficiency. For example, when the mechanical auxiliary transmission means 113 is formed by a transmission gear having a stepped switching structure, the rotation of the reaper 8 is freely increased by switching to a constant rotation near the maximum working speed, and the vehicle speed is synchronized. From the constant rotation to the constant rotation and the switch to turn on the pouring drive of the reaper 8 to selectively perform either the constant rotation or the pouring drive. As a result, the problem that two inputs having different rotational speeds are simultaneously transmitted to the mowing section 8 is eliminated, and in the structure in which the auxiliary transmission means using the variable hydraulic motor 106 is provided, the gear shifting of the mowing section 8 is changed from low to high. Even if the rotation speed of the mowing unit 8 is increased, the vehicle speed synchronization can be switched to a constant rotation in the middle of the rotation becoming excessively high, which improves durability and reduces driving noise. .

Further, in the combine in which the hydraulic transmission mechanism 107 for transmitting the power of the engine 21 is provided in the transmission case 23, a constant rotating shaft 71 is provided in the threshing section 4 below the threshing clutch 63 for transmitting the power of the engine 21,
A constant rotation mechanism 79 and a constant rotation clutch 78 that transmit the power of the constant rotation shaft 71 to the output side of the hydraulic speed change mechanism 107 are provided. Then, for example, by transmitting the output of the engine 21 to the output side of the hydraulic speed change mechanism 107 via the constant rotation mechanism 79 at the maximum work speed, the hydraulic pressure of the hydraulic speed change mechanism 107 is changed to the charge pressure to eliminate the hydraulic pressure change loss, and the hydraulic speed change mechanism is transmitted. 10
7 to reduce the power loss of traveling drive, improve the fuel efficiency of the engine 21, and form the oil cooler 29 of the hydraulic speed change mechanism 107 to have a small capacity, even if the traveling load becomes large, such as a direction change in a wetland. The operator performs a driving operation without feeling a lack of running power, reduces the output loss of the engine 21, and the like, recovers the power loss of the hydraulic speed change mechanism 107, and drives the running crawler at the highest speed with high efficiency. It is possible to improve the driving operability by enabling the highest speed work with a margin.

Further, when the working vehicle speed transmitted via the hydraulic speed change mechanism 107 becomes close to the maximum speed, the constant rotation clutch 78 is manually or automatically turned on to turn on the constant rotation clutch 78.
The increase in the vehicle speed (about 5%) by the difference between the volumetric efficiency (generally 75%) and the constant rotation output (generally 90%) of the hydraulic transmission 107 increases the vehicle speed. On the other hand, it requires less power,
The remaining engine 21 power is used to drive the working unit to secure the power required for the highest speed work, and a driving force of substantially the same rotational speed as the rotational speed at which the volumetric efficiency of the hydraulic speed change mechanism 107 becomes approximately 100%. By transmitting from the constant rotation mechanism 79 and designing the power of the engine 21 in accordance with the work maximum speed, there is a margin of power up to near the maximum speed, but when there is almost no margin of power at the maximum speed, The same effect can be expected when the engine 21 horsepower is increased by recovering the loss, and the power required for maximum speed work can be easily secured.

Further, when the working vehicle speed decreases from near the maximum working speed, the constant rotation clutch 78 is automatically disengaged, and the power of the engine 21 is designed to match the maximum working speed. Therefore, for example, even if the operator does not recognize that the work vehicle speed has decreased from the work maximum speed, the work vehicle speed can be reduced by simply performing an operation to reduce the work vehicle speed at the highest speed with almost no power. Due to the decrease, the highest speed working state is automatically released to improve the durability of the engine 21 and the fuel consumption.

Further, as shown in the flow chart of FIG. 20, the auxiliary shift lever 114 is operated at low speed or high speed.
When the threshing clutch lever 118 is operated to enter the threshing clutch 63, the feed chain solenoid 136 is kept off and the feed chain 5 is driven. When the reaper clutch lever 120 is operated at a low speed or a high speed to output the auxiliary gearshift at a low speed, when the reaper clutch lever 120 is operated to engage the reaper clutch 69, the reaper 8 is driven in synchronization with the vehicle speed. The reaper (8) is not driven when the auxiliary gear shift is high speed. In addition, the sink pedal 12
When stepping on 5 with your foot and turning it on, the pouring solenoid 1
37 is turned on, and the cutting unit 8 is turned on via the pouring gear 80.
When the grain culm sensor 132 is on and the cutting unit 8 is driven via the low speed gear 74 as shown in FIG. 14, the traveling (moving speed) detected by the vehicle speed sensors 130 and 131 is performed. Is below a certain level, or when the main shift lever 112 is operated to stop or reverse, the pouring solenoid 137 is automatically turned on, and all grain culms remaining in the reaping section 8 are transferred to the threshing section 4. The feed chain solenoid 136 is turned on and the feed chain 5 is automatically stopped when the harvesting section 8 has no grain culm and is not traveling forward and the harvesting section 8 is stopped.

Further, when the cutting gear shift lever 122 is operated to be neutral while traveling forward, the high speed cut solenoid 138 is turned on to drive the cutting section 8 via the high speed cut gear 81, and at the same time as shown in FIG. As described above, when the mowing gear shift lever 122 is not in the neutral position, the mowing unit 8 and the feed chain 5 are driven at a speed synchronized with the vehicle speed. Also, FIG.
Under the condition of No. 4, when the auxiliary shift lever 114 is on the low speed side and the mowing shift lever 122 is on the low speed side, the direct drive switch 129 is manually turned on, or when the vehicle speed is near the maximum work speed. , The cutting unit 8 is driven via the high speed cut gear 81, and the drive solenoid 139 is directly turned on to transmit the power from the high speed cut gear 81 to the output side of the hydraulic speed change mechanism 107 so that the traveling crawler 2 is driven via the high speed cut gear 81. Drive at high speed. Further, when the direct drive switch 129 is turned off, or when the vehicle speed decreases from the highest work speed, the direct drive solenoid 139 is turned off, the direct drive clutch 78 is manually or automatically turned off, and the high speed cut gear 81 is cut. Power is transmitted only to the part 8 side.

Further, as shown in FIG. 21, when the cutting unit 8 is driven through the high speed gear 75, the cutting input sensor 1
When the speed of rotation of the high-speed cutting gear 81 is reached by the cutting unit 8, the speed of rotation of the high-speed cutting gear 81 is stopped and the high-speed cutting gear 81 is automatically driven. Further, due to the rotation difference A between the high speed constant rotation of the high speed cut gear 81 and the standard cutting of the low speed gear 74, the constant high speed rotation reduces the hydraulic pressure of the hydraulic speed change mechanism 107 to improve the efficiency and drive the charge pump. When the amount of the difference A is set to zero, theoretically, the hydraulic speed change mechanism 107 does not perform the work for driving the mowing section 8, so that the mowing section 8 is mechanically driven only by the gears 80 and 81. The output of the engine 21 can be used with the drive loss of the hydraulic speed change mechanism 107 as power for the threshing unit 4. It should be noted that the maximum working speed B for high-speed mowing without high-speed cutting is approximately 80 to 50
The rotation speed of the high speed constant rotation C is set so that the rotation speed becomes a percentage.

[0041]

As is apparent from the above embodiments, the present invention is a combine in which the hydraulic transmission mechanism 107 for transmitting the power of the engine 21 is provided in the transmission case 23, and the harvesting section is synchronized with the vehicle speed via the hydraulic transmission mechanism 107. The vehicle speed tuning shaft 72 for driving the vehicle 8 and the constant rotation shaft 71 for directly transmitting the driving force of the engine 21 are provided.
And the constant rotation shaft 71 are selected to drive the mowing section 8. When the mowing operation reaches the maximum speed, the vehicle speed synchronized rotation is switched to a constant rotation, and the volumetric efficiency of the hydraulic speed change mechanism 107 is 100. When the reaping unit 8 is driven to rotate at a constant rotation at a percentage, the number of rotations at a constant rotation becomes higher than the rotation in synchronization with the vehicle speed, and the hydraulic speed change mechanism 107 does not perform the work of driving the reaping unit 8. The cutting machine 8 is driven by a good mechanical drive system, and the power of the engine 21 can be utilized for driving the threshing unit 4 by the loss of the hydraulic speed change mechanism 107, so that the efficiency of the harvesting work and the fuel consumption of the engine 21 can be easily improved. It can be achieved.

Further, the constant rotation shaft 71 for branching the driving force of the handling cylinder 6 and the vehicle speed tuning shaft 72 are installed in the counter case 32 in close proximity to each other substantially in parallel, and the pouring driving force for pouring the reaper 8 is operated. Is configured to be able to be input to the vehicle speed tuning shaft 72 from the constant rotation shaft 71. For example, the conventional belt transmission for transmitting the pouring drive force is not required, and the pouring drive structure of the reaper 8 is simplified and is compact and low in cost. Can be performed easily, the driving force for the pouring can be turned on and off by the pawl clutch 79 to prevent accompanying rotation, and the response delay can be reduced.
It is possible to prevent the clogging and reduce the loss of working time by driving the resin in a split manner.

Further, a harvesting speed change mechanism 73 for changing the drive speed of the harvesting section 8 is internally provided in the counter case 32, and the harvesting speed is switched in a state where the auxiliary shift is maintained at a standard (low speed), whereby the harvest grain is changed. Mowing work can be performed corresponding to the culm and the like. For example, there is no trouble of controlling the auxiliary shift changing means by the variable hydraulic motor 106 configured by changing the hydraulic motor of the hydraulic transmission mechanism 107, and the cutting transmission mechanism is provided. 73 can be switched even during work, and even when a part of the culm in the field is lying down, it is possible to change the vehicle speed synchronization speed of the mowing section to an appropriate speed, and the neutral of the mowing transmission mechanism 73 is also used as a mowing clutch. By doing so, it is not necessary to separately provide a reaping clutch, and the reaping input belt 45 is always tensioned to improve the durability.

Further, a rotational force equal to or higher than the rotational speed of the vehicle speed tuning input from the mission case 23 can be input to the vehicle speed tuning input shaft 72 from the constant rotation shaft 71. For example, the hydraulic motor 106 of the hydraulic speed change mechanism 107 is used. When the variable speed sub-transmission means is formed, the rotation of the mowing unit 8 is switched from the vehicle speed synchronization to the constant rotation when the working speed is the highest, so that the hydraulic pressure of the hydraulic speed change mechanism 107 is reduced by the difference in the number of rotations. The efficiency can be improved. For example, when the mechanical auxiliary transmission means 113 is formed by a transmission gear having a stepped switching structure, the rotation of the cutting section 8 can be freely increased by switching to a constant rotation in the vicinity of the maximum work speed. In addition, the switching from the vehicle speed synchronization to the constant rotation and the switching to turning on the pouring drive of the reaper 8 are selectively performed, and the constant rotation or the pouring drive is performed. By performing only one of the two, it is possible to eliminate the problem that two inputs having different rotational speeds are simultaneously transmitted to the reaper 8, and a structure is provided in which the auxiliary transmission means using the variable hydraulic motor 106 is provided. In the above, even if the gear shift of the mowing unit 8 is changed from low to high and the rotation speed of the mowing unit 8 is increased, it is possible to switch from the vehicle speed synchronization to the constant rotation in the middle of this rotation becoming excessively high. It is possible to easily improve the durability and reduce the driving noise.

Further, in the combine in which the hydraulic transmission mechanism 107 for transmitting the power of the engine 21 is provided in the transmission case 23, the threshing section 4 is provided with a constant rotation shaft 71 on the lower side of the threshing clutch 63 for transmitting the power of the engine 21 to perform a constant rotation. A constant rotation mechanism 79 and a constant rotation clutch 78 that transmit the power of the shaft 71 to the output side of the hydraulic speed change mechanism 107 are provided. For example, the output of the engine 21 is output to the output side of the hydraulic speed change mechanism 107 at the constant speed mechanism 79 at the maximum work speed. By transmitting via hydraulic pressure transmission mechanism 107, the hydraulic pressure of hydraulic transmission mechanism 107 can be used as a charge pressure to eliminate the hydraulic transmission loss, the power loss of traveling drive by hydraulic transmission mechanism 107 can be reduced, and the fuel consumption of engine 21 can be improved, and Hydraulic speed change mechanism 107
The oil cooler 29 can be formed to have a small capacity, and even if the traveling load becomes large, such as a change in direction in a wetland, the operator can perform a driving operation without feeling insufficient traveling power, and the output loss of the engine 21 can be reduced. Etc. can be easily achieved, the power loss of the hydraulic speed change mechanism 107 can be recovered, the traveling crawler can be driven with high efficiency at the maximum speed, and the maximum speed operation with a sufficient driving force can be performed to improve the driving operability. Can be easily achieved.

The constant rotation clutch 78 is manually or automatically turned on when the work vehicle speed transmitted via the hydraulic speed change mechanism 107 is close to the maximum speed. Vehicle speed (about 5%) by the difference between the volumetric efficiency (generally 75%) and constant rotation output (generally 90%)
However, since the power required for increasing the vehicle speed is small, the remaining power of the engine 21 can be used to drive the working unit, and the power required for the highest speed work can be easily secured.

Further, the constant rotation mechanism 79 transmits a driving force at a rotation speed substantially the same as the rotation speed at which the volumetric efficiency of the hydraulic speed change mechanism 107 becomes approximately 100%, and the power of the engine 21 is designed to match the maximum work speed. As a result, there is a margin of power up to near the maximum speed, but when there is almost no margin of power at the maximum speed, the same effect is expected when the engine 21 horsepower is increased by collecting the power loss. It is possible to easily secure the power required for the highest speed work.

Further, the constant rotation clutch 78 is automatically disengaged when the work vehicle speed decreases from around the maximum work speed. By designing the power of the engine 21 to match the maximum work speed, the maximum speed near the maximum work speed can be achieved. Because there is plenty of power,
For example, even if the operator does not recognize that the work vehicle speed has decreased from the maximum work speed by only performing an operation that reduces the maximum work vehicle speed with almost no power, the maximum work speed decreases due to the decrease in the work vehicle speed. The working state can be automatically released, and the durability of the engine 21 and the fuel consumption can be easily improved.

[Brief description of drawings]

FIG. 1 is an overall side view of a combine.

FIG. 2 is a plan view of the same.

FIG. 3 is a front view of a threshing unit and an engine mounting unit.

FIG. 4 is a side view of the same.

FIG. 5 is a plan view of the same.

FIG. 6 is an engine output system diagram.

FIG. 7 is an enlarged view of the main part.

FIG. 8 is a side view of the counter case.

FIG. 9 is a plan view of the same.

FIG. 10 is a sectional view of the same.

FIG. 11 is a partially enlarged view of the previous figure.

FIG. 12 is a transmission system diagram of a counter case.

FIG. 13 is an explanatory view of the same transmission.

FIG. 14 is an explanatory diagram of vehicle speed synchronization.

FIG. 15 is an explanatory diagram of the high speed cut and direct drive.

FIG. 16 is an explanatory diagram of the high speed cut.

FIG. 17 is an explanatory view of providing a gear type auxiliary transmission mechanism.

FIG. 18 is an explanatory view of providing a variable hydraulic motor.

FIG. 19 is a control circuit diagram of harvesting work.

FIG. 20 is a flowchart of harvesting work control.

FIG. 21 is a drive output diagram of the mowing unit.

[Explanation of symbols]

4 Threshing Department 6 handle 8 reaper 21 engine 23 mission case 32 counter case 63 Threshing clutch 71 constant rotation axis 72 Vehicle speed tuning axis 73 Mowing speed change mechanism 78 Direct drive clutch (constant rotation clutch) 79 Constant rotation mechanism 107 Hydraulic speed change mechanism

Claims (8)

[Claims] 1. In a combine in which a hydraulic speed change mechanism for transmitting power of an engine is provided in a transmission case, a drive speed of an engine and a vehicle speed tuning shaft for driving a reaper in synchronization with a vehicle speed via the hydraulic speed change mechanism are directly provided. A combine, which is provided with a constant rotating shaft for transmitting, and selects either the vehicle speed tuning shaft or the constant rotating shaft to drive the reaper. 2. A constant rotational speed for branching the handling cylinder driving force,
The vehicle speed tuning shaft and the vehicle speed tuning shaft are installed in the counter case so as to be substantially parallel and close to each other, and a pouring driving force for pouring the cutting unit can be input from the constant rotation shaft to the vehicle speed tuning shaft. Combine as described in. 3. The combine harvester according to claim 2, wherein a harvesting transmission mechanism for changing the drive speed of the harvesting section is internally provided in the counter case. 4. The combine according to claim 1, wherein a rotational force equal to or higher than the rotational speed of the vehicle speed tuning input from the mission case can be input to the vehicle speed tuning input shaft from a constant rotation shaft. 5. In a combine in which a hydraulic transmission mechanism for transmitting engine power is provided in a transmission case, a constant rotating shaft is provided on a lower side of a threshing clutch for transmitting engine power in a threshing section, and the power of the constant rotating shaft is hydraulically shifted. A combine which is provided with a constant rotation mechanism and a constant rotation clutch which are transmitted to the output side of the combine. 6. The combine according to claim 5, wherein the constant rotation clutch is manually or automatically turned on when the work vehicle speed transmitted via the hydraulic speed change mechanism is close to the maximum speed. 7. The combine according to claim 5, wherein the constant rotation mechanism transmits a driving force at a rotation speed substantially the same as the rotation speed at which the volumetric efficiency of the hydraulic speed change mechanism becomes approximately 100%. 8. The combine according to claim 5, wherein the constant rotation clutch is automatically disengaged when the work vehicle speed decreases from near the work maximum speed.